Method and means for mounting, driving and supporting rolls for endless moving bands



Feb. 2, 1965 E. D. BEACHLER 3,168,435

METHOD AND MEANS FOR MOUNTING DRIVING AND SUPPORTING ROLLS FOR ENDLESS MOVING BANDS Filed Nov. 25. 1960 3 Sheets-Sheet l PIE/OE ABT FYqz/ 03490 LILJLi/lj/LJLILJLILI IN V EN TOR.

Edward 0. Beach/er A TTORNE YS Feb. 2, 1965 E. D. BEACHLER 3,158,435

METHOD AND MEANS FOR MOUNTING DRIVING AND SUPPORTING ROLLS FOR ENDLESS MOVING BANDS Filed Nov. 25. 1960 3 Sheets-Sheet 2 IN V EN TOR. f'darard 0 Bear all/er A TTORNE YS Feb. 2, 1965 E. D. BEACHLER 3,168,435

METHOD AND MEANS FOR MOUNTING DRIVING AND SUPPORTING ROLLS FOR ENDLESS MOVING BANDS Filed Nov. 25, 1960 3 Sheets-Sheet 3 f e Q$S e N3 Q mm emm .63 M M o amQ o R\ o NQ o B a A U I u I! I I \QQ\ l d o mm \m R 68 a 0 mm o W Q um m ATTORNEYS United States Patent 3,168,435 METHOD AND MEANS FOR MGUNTIN G, DRIVING AND SUPPORTING RQLLS FOR ENDLESS MOV- ENG BANDS Edward D. Beachler, Beloit, Wis, assignor to Beloit Corporation, a corporation of Wisconsin Filed Nov. 25, 19%, Ser. No. 71,685 13 Claims. (Cl. 162-648) The present invention relates broadly to the paper making and related arts, and is more particularly concerned with a roll structure provided with shaft means operatively engaging the roll interior inwardly from one edge thereof and having a shaft portion extending outwardly from said edge, the shaft means effectively functioning to relieve the normal central deflection in the roll.

It is known that at different stages during the course of paper manufacture roll structures of various types are employed for performance of diverse functions. Illustrative of such rolls are wire drive rolls, press rolls, pressure rolls, breaker stack rolls, pull rolls, calender rolls, felt rolls and the like. Each of the mentioned types of rolls has in common, for the purpose of the instant description, the use therewith of means normally contacting the roll and tending to deflect the centroidal axis thereof.

To illustrate, drive rolls mounted to engage the loop of the forming wire in a Fourdrinier type paper making machine engage the surface of the wire, and the weight of the roll coupled with an applied load arising from the resistance of the wire to being driven produce a force component which tends to deflect the drive roll in a direction downwardly and toward the oncoming forming wire. As well, in press roll couples and in other roll arrangements wherein at least a pair of rolls are in nip-defining relationship, the algebraic summation of the weight, the nip forces, the bending moments produced by the journal loading, and torque (if any) tends to produce in each of such rolls a curvature of its centroidal axis, in accordance with well known laws of flexure of materials. It is common to attempt to counter this effect by crowning, i.e., by grinding the roll slightly barrel shape in an amount and curvature calculated to offset the curvature under operatingconditions.

The normal deflection, when concave toward the wire wrap, on a wire drive roll, it not relieved, tends to cause the off-running portion of the forming wire to be compacted or squeezed laterally, which increases substantially the wear on the wire. The initial investment in a forming wire is very substantial, but even more important, the production loss during wire replacement is frequently enormous.

Specifically as to press rolls, a different problem exists. Production schedules for many paper machines require relatively frequent changes in the type and grade of product. Certain grades of paper demand that the pressing and other treatment not reduce significantly the thickness or caliper of the web, and this in turn requires that the nip loads in a press couple be relatively light. .On the other hand, certain other paper products required from the same paper machine permit or even demand more severe pressing, and in order to achieve some measure of versatility with the same paper machine, one practice followed by the art toaccomplish the noted changes is the removal of the press rolls for regrinding to a different amount of crowning. Obviously, this practice is also both expensive and-time consuming. And as will be later noted, crowning of the roll causes differences in the surface speed of the roll between the central and end portions of the roll, which is often harmful to the function of the press.

3,168,435 Patented Feb. 2, 1965 It is accordingly an important aim of the instant invention to provide a roll assembly embodying therein novel means to counteract the forces tending to deflect the roll.

Another object of this invention lies in the provision of an improved paper machine arrangement comprising a roll shell having normally a central deflection, bearings rotatably mounting the roll shell, and shaft means for the roll shell operatively engaging the interior of the shell inwardly from one edge thereof and having a shaft portion extending outwardly from said edge, said shaft means relieving the normal deflection.

Still another object of the present invention is to pro vide an improved paper machine which includes a traveling band, a roll engaging the band and having normally a central deflection, shaft means for said roll, bearing means receiving said shaft means, and means applying a force to the shaft means to relieve the normal deflection in the roll.

A further object of this invention lies in the provision of an improved paper machine construction comprising a looped forming wire, a shaft supported roll engaging the wire, bearing means receiving the-shaft at one or more locations therealong, and means associated with the bearing means for applying a force thereto to deflect the shaft and accordingly the central portion of the roll to relieve the normal deflection and to induce an opposite deflection when desired.

A still further object of this invention is to provide a method of deflecting a roll, which comprises engaging a traveling band with a roll, and bowing the shaft for the roll at a location between opposite ends of the shaft to deflect the central portion of the roll.

An even further object of this invention lies in the provision of a method of driving a looped forming wire in a paper machine, and which includes the steps of engaging the wire with a drive roll, rotating the roll to drive the wire, and applying a force initially to the roll at a point remote from the central portion thereof to deflect said portion in a direction opposite to its normal deflection.

Other objects and advantages 'of the invention will become more apparent during the course of the following description, particularly when taken in connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughout the same:

FIGURE 1 is a substantially diagrammatic view in side elevation of a paper machine of the Fourdrinier type;

FIGURE 2 is a diagrammatic view illustrating forces which are applied to a drive roll in the paper machine of FIGURE 1;

FIGURE 3 is an essentially diagrammatic top plan view, slightly exaggerated, of a drive roll mounting of the prior art;

FIGURE 4 is a substantially diagrammatic view in side elevation of the mounting of FIGURE 3;

FIGURE 5 is a diagrammatic top plan view drawn along the lines of FIGURE 3, and showing an illustrative embodiment of the instant invention;

FIGURE 6 is a top plan view along the lines of FIG- URES 3 and 5, and illustrating a further embodiment of the present invention;

FIGURE 7 is a vertical sectional view, with parts in elevation, through varying means which may be employed to accomplish the novel purposes of the present invention;

FIGURE 8 is a more or less diagrammatic viewyof a portion of a drying section in a paper machine, and showing the instant deflection relieving-means applied to a felt roll;

FIGURE 9 is a diagrammatic view of a calender stack and illustrating roll deflection structure forming a part of the king roll of the calender stack;

FIGURE is a diagrammatic elevational view of. a press roll coupled and wherein means are provided for controlling the nip pressures therein; and

FIGURE 11 is a. view in end elevation, with parts thereof taken in section, and showing deflection relieving means used with a roll shell and stationary shaft means therefor.

The description now to follow will be first directed to means for counteracting the forces tending to deflect a wire drive roll. However, it is to be emphasized and as will be later'brought out, the instant invention is not restricted to a wire drive roll. In fact, the invention is of important application to any roll structure, whether or not used on or off a paper machine, and it is within the contemplation of this invention that the deflection relieving means herein disclosed will produce substantial improvements on rolls used in steel mills and other industries.

Referring now to the drawings, there is shown in FIG- URE 1 a paper machine generally designated by the numeral 10 and comprising a head box 11 for flowing stock onto the upper or top run 12a of a looped forming wire 12; The top run 12a of the forming wire extends from a breast roll 13 over table rolls 14 and suction boxes 15 to a couch roll 16. The wire 12 is then directed around a turning roll 17 and over and under return end guide rolls, 18, 19, 20 and 21 back to the breast roll 13. In the paper machine illustrated, the roll 20 mounted outside the loop of the wire 12 is a roll which drives said wire.

A diagram of some of the forces which are applied to the roll 20 is shown in FIGURE 2. The wire 12, which travels in the direction indicated by the arrow, passes over the top of the roll 20 and wraps said roll by a total angle of wrap of 2 alpha. The oncoming side 12b of the wire wraps the roll 20 over the angle alpha, and the off-running side 120 of the wire also wraps the roll over the angle alpha, with the dividing line v therebetween being essentially a vertical line passing through the radial center of the roll 20. The tension on the wire 12 accordingly applies a force in an essentially vertical downward direction indicated by the arrow A.

A force in the direction of the arrow A is also applied by the weight of the roll 20. As is appreciated, the loading forces such as the tension on the wire 12 and the weight of the roll load the roll 20 as a beam. Further, the roll 20 has a substantial length in comparison to its diameter, and in a typical paper machine the roll 20 is approximately 20 feet in length, while its diameter may not be greater than 1 /2 feet.

It will also be appreciated that a load is applied across the top of the roll in a direction generally tangential to the roll portion wrapped by the wire 12, when the roll 20 is rotated in the direction indicated by the arrow thereon. The wire resists being driven to this extent so as to apply this load to the roll 20, and the load applies generally in the direction of the line of force B. The force line C indicates the resulting sum of all of the loads applied to the roll 20, and this force line is generally the direction in which the roll 20 tends to deflect in the central portion thereof. It is to be seen from FIGURE 2 that the roll tends to deflect in a direction downwardly and toward the oncoming wire 12b.

The deflection which occurs is shown in somewhat exaggerated form in FIGURES 3 and 4. In the former view,

the roll 20 is shown with one journal 22 rotatably mounted in drive means 23, and the other journal 24 mounted for rotation in bearing means 25. The wire 12 passes over the top of the roll 20, and it is to be seen that the roll 20 deflects in its central portion '20arearwardly or in the direction of the oncoming side 12b of the wire 12. V

As is shown in FIGURE 4, the central portion 200 of the roll 20 deflects off-center from the drive means 23 and from the extreme edge of the roll, identified in full line and marked 20. Thecentral portion 20a is deflected toward the oncoming side 12b of the wire and aiso in a downward direction. The result is that the central portion of the wire 12 drags as it passes over the roll 20, and this deflection is also believed to result in the application of transverse forces to the wire, in essentially directions indicated by the arrows E of FIGURE 3.

Accordingly, although the oncoming side 1212 of the wire 12 may have no transverse forces applied thereto, and the wire 12 may be traveling in substantially a straight line in a plane generally tangential to the roll 20 as indicated in FIGURE 3 by the arrows b, there is a tendency for the edges of the wire at the off-running side 12c to be urged inwardly as indicated by the arrows c once the wire passes over the bowed or deflected roll 20. While it may be that there are a number of explanations for the described action, the theory set forth provides a running wire side 120 provides an opportunity for the wire to ridge, especially if any slight forces are applied normal to the plane of the wire. Such forces could originate in various ways, as for example, by fibers or dirt or impurities adhering to the roll 20 and passing between said roll and the forming wire 12.

Referring now particularly to FIGURE 5, there is shown one embodiment of the present invention which is a drive roll arrangement indicated generally by the reference numeral 30. In the arrangement 30 shown, a drive roll 31 is freely supported upon a shaft by a rigid connection 33 interiorly of the drive roll 31, which connection may be in the form of a collar welded or otherwise secured to one end of the shaft 32 and to the inner diameter of the drive roll 31. In the arrangement of FIGURE 5, the rigid connection 33 is made outwardly of the center of the length of the drive roll 31, and preferably approximately one-half of the distance from the drive roll end 31a inwardly toward the center of the length of said drive roll, i. e., within substantially the middle one-half of the overall shell transverse or cross-machine direction. The arrangement 30 may be adapted for relatively short length drive rolls by locating the rigid connection 33 centrally of the length of roll 31, although it is to be appreciated that an arrangement essentially identical to that indicated by the numeral 30 is located at the opposite end of the drive roll 31 for applications to usual roll lengths.

The drive shaft 32 is driven by suitable drive means 34 (shown diagrammatically), and said shaft 32 is journaled in a plurality of bearing means 35, 36 and 37.

Each of the bearing means 35, 36 and 37 is of the selfaligning type, an exemplary construction of which will be later described in connection with FIGURE 7 and it is to be seen from FIGURE 5 that the bearing means 35 is forces in opposite directions to the bearing means 35, and

conections 43-43 are made to the actuator to supply hydraulic fluid, air under pressure or the like. It is, of course, appreciated that the use of actuator means to apply forces to the bearing means 35 is illustrative only, and that other means may be employed for this purpose.

7 The bearing means 36 is shown as carried in a suitable frame or other support 44 rigidly attached to suitable structure, and the bearing means 37 is mounted slightly inwardly of one end of the drive roll 31 and suitably attached to the inner diameter of said drive roll. A wire 45 passes over the roll 31 and is driven thereby in the direction indicated by the arrows in FIGURE 5.

The roll 31 would normally have a central deflection, that is, the weight load, tension load and load imposed by driving of the wire 45 tend to deflect the roll 31 in the central portion thereof. However, by utilization of the actuator means and bearing means of this invention there is counteracted the tendency of the drive roll to deflect. As for example, if the drive roll 31 has a tendency to deflect in its central portion to generally the configuration of FIGURE 3, the actuator 42 is operated to retract the piston member 41, which force when applied through the bearing means 35 deflects the shaft 32 in the region of the bearing means in the same direction as the force applied by the actuator 42. This direction is shown in arrows in FIGURE 5 adjacent the bearing means 35, and this bowing in the shaft 32 is transmitted in the opposite direction through the bearing means 36 and 37 and is applied against the drive roll 31 in the region of the rigid connection 33 to essentially entirely overcome the tendency of the roll 31 to deflect, with the result that the roll 31 is essentially entirely straight throughout its length. It will be appreciated, however, that by application of an even greater force by the actuator means 42, the drive roll 31 can be deflected an even greater amount whereby said roll is deflected centrally in generally the direction of wire travel. Since it is diflicult at times to compensate precisely for the tendency of the roll 31 to deflect, as when during operation of the wire 45 changes in its tension'occur, it is desirable to overcornpensate for this deflection tendency in the manner just indicated.

As is shown in FIGURE 5, the oncoming side of the wire 45 does not have any transversely aligned forces applied thereto, and by maintaining the roll 31 in a substantially undeflected alignment (as shown in FIGURE 5) by the drive arrangement of this invention, the OE- running side 45b of the wire 45 also has no transverse forces applied thereto, and the wire leaves the top of the roll 31 in a generally tangentially aligned plane as indicated by the arrows d.

The drive arrangement 30 of FIGURE 5 has especial utility with drive rolls of relatively shorter lengths and in those cases wherein it is desired to compensate exactly for the tendency of the roll 31 to deflect. Another embodiment of the invention, and which is particularly adapted for relatively longer drive rolls and to apply a slightly distorting force to the forming wire, is shown in FIGURE 6, to which reference 'is now made.

As shown, a drive arrangement generally indicated by the reference numeral 46 is provided, and utilized therein is a plurality of bearing means and actuator means of essentially the same character identified in FIGURE 5 by the numerals and 42, respectively. Accordingly, in the arrangement of FIGURE 6 like numerals accompanied by the suffix a, b, c and d has been appended to designate like parts. A drive roll 47 is provided with a shaft 48 at opposite ends thereof journaled in bearing means 35a, 35b, 35c and 35d, a pair of said bearing means being provided at the opposite ends of said shaft 48. Suitable drive means (not shown) is provided at either or both ends of the shaft 48 to rotate the shaft and drive roll in the direction indicated.

A wire 49 passes over the top of the roll 47 and has an oncoming side 49a and an off-running side 4%. his to be seen upon reference to FIGURE 6 that the bearing means 35a-d have forces applied thereto by actuator means 42a-d sufficient to actually deflect the central portion 47a of the roll '47 in the direction opposite to the direction in which the roll 47 would normally tend to deflect. This may be accomplished by the actuators 42a and 42d applying a rearward and downward forceto the bearing means 35a and 35d, and the actuators 42b and 42c applying an upward and forward force to the bearing means 35b and 35c, respectively. As is now apparent, essentially the same result may be accomplished by rigidly mounting the bearing means 35a and 35d, and applying the-forward and upward forces to only the bearing means 35b and 35c. Further, lesser forces may be applied to the bearing means by the actuator means so that the central portion 47a of the roll 47 is deflected to a lesser extent whereby all portions of the roll are essentially in the same vertical plane. In addithe expedient.

tion, the forces applied by the actuator means to the bearing means and accordingly the various portions of the shaft or journal 48 may be varied to provide the drive roll 47 with various other deflections to serve a particular purpose.

The advantage of the mounting 46 for the roll 47 is that this roll is so deflected in the central portion 47a that it applies outwardly directed transverse forces to the off-running wire 45b along the lines -indicated by the arrows e. At the oncoming side the wire 47a is in substantially straight line alignment as indicated by the arrows f, but when it passes over the roll 47 it is actually spread transversely ever so slightly. This slight application of outwardly directed transverse force not only makes certain that a change of operating conditions will not result in the application of inwardly directed transverse forces, but in addition, renders certain that particles ofdirt, fibers and the like which may pass between the roll 47 and wire 49 will not normally impart forces normal to the plane of the wire of such magnitude as to cause ridging or other damage to the forming wire. Stated otherwise, it has been discovered that it is actually advantageous to apply a slightly distorting force to the wire 49 as it passes over the drive roll 47, as long as these forces are outwardly directed transversely to the travel of the wire.

Various forms of self-aligning bearing means available to the trade may be employed in the practice of the present invention, and illustrated in FIGURE 7 is an exemplary bearing means 35. The bearing means is provided with an annular strap portion 50 having a concave segmental spherical inner face or bearing wall 51 cooperating with aconvex segmental spherical outer bearing 'wall 52 on an outer race ring 53. The ring 53 has a ball groove or raceway 54 formed around its inner periphery intermediate the sides of the ring to receive a row of ball bearings 55. An inner race ring 56 extends through the outer race ring 53 in radially spaced relationship therewith, and has an external ball groove or raceway 57 therearound to receive the row of ball bearings 55. The ball bearings 55 and the raceways 54 and 57 cooperate to hold the rings 53 and 56 against relative axial movement but in radial spaced apart relationship. The rings rotate freely relative to each other on the row of ball bearings 55. The outer ring 53 can tilt in the strap 59 to accommodate for misalignment between the shaft 32 or 48 and the framework 39 (FIGURE 5) attached to the annular strap 50. Set screw meansor the like 58 secures the inner race ring 56 to the shaft 32. Seal means of the character indicated by the reference numeral 59 may be employed to provide a sealed ball chamber D.

It has been earlier emphasized that the instant invention is not limited to wire drive rolls, but is also productive of new and novel results when applied to felt rolls, calender stacks, press rolls and the like, and in fact to any roll Whose centroidal axis tends to deflect for any one or a number of reasons. This'is shown in FIGURES 8 to 111, wherein reference is first made to FIGURE 10.

As appears in FIGURE 10, a press roll couple generally designated by-the numeral 60 comprises a top press roll '61 and bottom press roll 62 defining therebetween a hip N. At the nip N it is necessary to apply different loads for different grades of paper, and it is further desirable'that it be possible to produce different grades on the same paper machine. Furthermore, it is often desirable to alter the nip-loading for other reasons. However,

to accomplish this it has previously been required to remove the press rolls for regrinding to a different amount of crowning, crowning of course being practiced in an endeavor to obtain uniform nip loads across the contacting roll faces or to accept a degree of non-uniformity as To remove the press rolls and to effect regrinding is obviously a time consuming and expensive procedure.

These difliculties are herein eliminated by journaling shaft means 63 at opposite ends of the top press roll 61 in fixedly mounted self-aligning bearing means 64 and 65 structurally corresponding to the bearingmeans 36 of FIGURES. In addition, shaft means 66 for the lower press roll 62 is journaled at opposite ends in a pair of self-aligning bearing means to which forces are applied by actuator means, the bearing means and actuator means of FIGURE 10 structurally corresponding to like means SSa-d and 42a-d of FIGURE 6, and accordingly, like numeralsraised by 100 have been applied to like parts in FIGURE 10.

' It is now believed apparent that by exerting through the actuator means 142b and 1420 an essentially vertical upward force on the respective bearing means 135).; and 1350, and an essentially vertical downward force on the bearing means 135a and 135d through the actuator means 142a and 142d, the forces normally creating deflection of the centroidal axes of the press rolls 61 and 62 are effectively balanced. Of course, the deflection relieving forces applied to the lower press roll 62 are transferred therethrough to the top press roll 61, which as noted, is provided with bearings 64 and 65 which are fixedly mounted. It is believed likewise evident that the forces applied to the lower press roll 62 can be in excess of those required to balance the forces normally creating the deflection, and that by manipulating the fluid forces to the actuator means 142, either an under-compensation or an over-compensation may be provided which permits the adjustment of the nip pressure distribution profile to provide a higher value at the ends with respect to the midspan, or a lower pressure value at the ends.

The inventive concept described in connection with FIGURE 10 may also be applied to a calender stack, as appears in FIGURE 9. This provides a great increase in the versatility of a calender stack, permitting the papermaker to quickly and conveniently compensate for inevitable variations in the paper web, which compensation has never previously been available to him.

Referring now to FIGURE 9, there is shown a calender stack generally designated by thenumeral 70 and comprising a bottom or king roll 71 and a plurality of relatively smaller diameter rolls 72-75 in general vertical alignment therewith. As is the practice in the art, the calender stack 70 is supported by a suitable frame (not shown).

It is also known that the king roll 71 carries the weight of the rolls 72-75 and the bearings therefor, and accordingly, it has been the prior art practice to crown the king roll 71 to compensate for its deflection and to thereby attain generally uniform nip pressures. However, crowning is a relatively expensive machining operation, and eventually recrowning is necessary because of gradual wear on the king roll. In addition, and as is known to those skilled in the art, the different peripheral speeds along various portions of a roll is often disadvantageous in press applications, and of course, a particular crown is only satisfactory for a specific load condition.

These problems are herein avoided by provision of deflection relieving means generally designated in FIG- DRE 9 by the numeral 80. Such means is more or less diagrammatically shown and desirably takes the form of the bearing and actuator structure identified in FIGURE .5 by thenumerals 35 and 42. Accordingly, where space permits like numerals raised by 200 have been applied to like parts in FIGURE9. As well, and although not shown, the rolls 7275 at opposite ends thereof have their shaft means journaled in fixedly mounted selfaligning bearing means of the character designated at 64 and 65 in FIGURE 10. As is known, in a calender stack arrangement it is the combined weights of the rolls 7175 which tend to deflect the king roll 71, and in accordance with the instant teachings, there is applied to the king roll 71 by the deflection relieving means 80 a force generally equal tothe nip load at N4 and the weight of the king roll.

Of course, the bearing and actuator structure for the king roll 71 may correspond to either the means 35, 36, and 42 of FIGURES, or the means 3511-41 and 42ad of FIGURE 6. Generally, however, in view of the sub stantial size and weight of the king roll 71, the bearing and actuator, arrangement of FIGURE 6 would normally be employed.

The preceding description has been directed to deflection relieving means associated with rotatable shafts, however, as will now be noted in connection with FIG- URES 8 and 11, effective results are also obtained'when the instant concept is applied to stationary shaft means. To explain, and by way of illustration, in the dry end section of paper machine drying apparatus the traveling paper web is urged against the surfaces of successive drying cylinders by continuous felts, which of course absorb some of the web moisture. The felts are guided during their travel by felt rolls, and in modern high speed paper machines it has been found desirable for high drying efliciency that the felts be constantly under tension.

This general environment is shown in FIGURE 8, which diagrammatically illustrates a portion of a dry end section of drying apparatus for a paper machine. This portion of the dry end section is identified generally by the numeral and may be seen to comprise a first row of horizontally aligned drying cylinders or drums 86a, 86b, etc.', and a second row of horizontally aligned drying cylinders 87a, 87b, etc. A web of paper W passes alternately about the drying cylinders 86 and 87, and is maintained in contact with the surfaces of the drying cylinders 86 by a felt 88, and against the surfaces of the drying drums 87 'by a felt 89. A suitable number of rollers are arranged to guide the felt 88, and rollers 91 guide the felt 89.

As was stated, eflective web moisture removal is enhanced when the felts 88 and 89 are under a moderate constant tension, and in accordance with the instant teachings, the'tension is applied by deflecting or bowing one or more of the felt rolls 90 or 91'. Means for this purpose is identified generally in FIGURE 8 by the numeral 92, the structural details of which appear in FIG- URE 11.

A felt roll 91 may comprise a shell member 93 having reduced diameter end'portions 93a and 93b journaled in bearing means 94 and 95, the construction of which may be seen to be identical. The description of one will accordingly sutfice for the other, and it may be seen that the bearing means 94 comprises a housing 96 fixedly mounted by suitable structure and mounting therewithin inner and outer races 97 and 98 receiving therebetween ball means 99.

The means 92 for bowing the roll shell member 93 or for relieving any central deflection therein caused by its own weight or other factors, further comprises shaft means 100 extending outwardly from opposite ends of the shell member and supporting generally centrally of the axial length of the shell member 93 a bearing member 101, which make take the form of self-aligning bearing means of the character indicated at 37 in FIGURE-5. Of course, the inner race ring of the bearing means 101 is secured to the shaft 100, as byfset screw means as earlier referred to at 58 in connection with FIGURE 7.

The shaft means 100 through the bearing means101 may thus be seen to operatively engage the inner diameter of the'roll member 93, and to have shaft portions 100a and 10012 extending outwardly from the opposite open ends of the shell member 93. The shaft-means 100 ,is non-rotatable, and each of the shaft end portions 100a and 10015 is mounted in a pair of bearing'means 102a-b and 103a-b. The bearing means 102a-b are fixedly mounted by suitable structure, as shown, and these bearing means are of the self-aligning type which can take the form shown in detail in FIGURE 7. The bearing means 103a-b, on the other hand, are also of the selfaligning type, and connected IhBIdO; are actuator means 9 104a-b. It may accordingly be seen that the bearing means 103a-b andactuator means 104a-b are structurally the same as the means 35 and 42 of FIGURE 5, and that the fixed bearing means 102a and 10212 structurally correspond to the bearing means 36 of FIGURE 5.

"It is now believed apparent that through provision of thefixedly mounted self-aligning bearing means 102a-b, the operative engagement of the shaft means 100 withthe roll shell inner diameter through the bearing means 101, and by the movable bearing means 103mb and associated actuator means ltMa-b, generally vertical and upward forces applied to the bearing means 103 'in the direction indicated by arrows causes a force to be exerted which relieves the normal deflection of the centroidal axis of the shell member '93. The'force applied may only be suflicient to match or balance the force tending to deflect the centroidal axis of the roll member 91, or a relatively larger force can be applied to over-deflect the roll in order to apply even greater tension to either of the felts 88 or 89. Of course, the arrangement of FIGURE 11 is not restricted to felt rolls, and it may be found upon occasion that the bearing means 103a-b and actuator means 164ab are not required, and that the normal central deflection of the shell member 93 is sufliciently relieved by the central bearing means 101, shaft means 100 and fixed bearing means 102ab. Thus, by supporting opposite ends of the stationary shaft 100 in the bearing means 102a-b, by supporting the weight of the shell member 93 in the fixed bearing means 94 and 95, and by operatively engaging the roll inner diameter at 101, without use of the bearing means 103a-b and actuator means 104a-b, suflicient positive support is provided to overcome any tendency of the shell member 93 to deflect. Of course, more than a single bearing member 101 may be utilized for particular applications.

This application is a continuation-in-part of my pending application, Serial No. 772,392, filed November 4, 1958.

Various forms of deflection relieving means have been illustrated in the drawings and described herein, and it is accordingly believed quite apparent that this invention is susceptible of numerous modifications without departing from the novel concepts thereof.

I claim as my invention:

1. Apparatus comprising, a roll shell having a substantial length-to-diameter ratio, means for applying a load along the transverse dimension and perpendicular to the axis of said shell for imparting thereto normally a central deflection, bearings rotatably mounting said roll shell, drive shaft means for co-rotation with the roll shell operatively and drivingly engaging the interior of the shell inwardly from one edge thereof within substantially the middle one-half of the shell transverse dimension and having a shaft portion extending outwardly from said edge, and axially spaced means exterior of the shell exerting a force couple on said shaft portion for transmission of force via the operative engagement between the interior of the shell and the shaft, thereby relieving such normal deflection in the shell, said axially spaced means imparting a deflection to said shaft portion in-teriorly of the shell from said shaft portion extending outwardly from the edge of the shell.

2. In a paper machine, a traveling band, a roll engaging and supporting the band and having normally a central deflection, shaft means for said roll, bearing means receiving said shaft means, and axially spaced relatively movable fluid actuated means engaging said bearing means applying a force couple to said shaft means to relieve the normal deflection in said roll.

3. In a paper machine, a traveling band, a roll engaging and supporting the band and having normally a central deflection, shafit means for said roll, bearing means receiving said shaft means, and axially spaced relatively movable means applying a force couple to said shaft via said bearing means to deflect said shaft means and relieve the normal deflection in said roll.

4. In a paper machine, a looped forming wire, a roll engaging and supporting the wire and having normally a central deflection, shaft means for said roll, bearing means receiving said shaftrmeans, andaxially spaced relatively movable fluid actuated meansengaging said bearing means applying a force couple to :said shaft via said bearing means to deflect said shaft means and relieve the normal deflection in the central portion of said roll.

5. In a paper machine, a looped forming wire, .a roll engaging and supporting the wire and having normally a central-deflection, shaft means for said roll, bearing means receiving said shaft means, and axially spaced relatively movable means connecting with the bearing means and applying a force thereto to how the shaft means and roll slightly in a direction opposite to the normal deflection of the roll.

6. In a paper machine, a looped forming wire, a drive roll engaging the wire and having normally a central deflection, shaft means for said roll, a plurality of selfaligning bearing means receiving said shaft along at least one end thereof, and means connecting with at least one of said bearing means to apply a force thereto away from the direction of normal central deflection of the roll to bow the shaft means and roll in a direction opposite to normal deflection of said roll.

7. In a paper machine, a looped forming wire, a drive roll engaging the wire and having normally a central deflection, shaft means connecting inwardly from one end of the roll and outwardly of the center of the length of said roll, self-aligning bearing means receiving the shaft along the opposite end thereof, and actuator means connecting with the bearing means applying a force thereto in one direction to bow the shaft means and roll adjacent its connection to the shaft in a direction opposite to normal deflection of said roll.

8. In a paper machine, a looped forming wire, a drive roll engaging the wire and having normally a central deflection, a shaft rigidly connected to the roll between one end of the roll and the center of the axis of said roll, drive means at the opposite end of the shaft for rotating said roll and driving the wire thereover, bearing means connecting with the shaft between the drive means and one end of the roll and tiltable upon application of a force thereto to bow the shaft in the direction of said force, and means for moving the bearing means in at least one direction to how the shaft and roll adjacent its rigid connection to the shaft to deflect the roll in a direction opposite to its normal deflection.

9. In a paper machine including a drive roll, shaft means therefor, and a forming wire passing over the top of the roll, the improvement which comprises a plurmity of self-aligning bearings receiving said shaft along one end thereof, and means applying a force to at least one of the bearings to bow the shaft and deflect the roll to correct for normal deflection thereof.

10. In a paper machine including a drive roll, shaft means therefor, and a forming wire passing over the top of the roll, the improvement which comprises a plurality of self-aligning bearings receiving said shaft at opposite ends thereof, and means connecting with each of the bearings and applying a force couple in one direction to at least one pair of bearings to how the shaft and roll to deflect the roll in the central portion thereof in a direction opposite to its normal deflection.

11. A method of driving a looped forming wire in a paper machine, which comprises engaging the underside of said wire with a drive roll, rotating the roll to drive the wire, and applying a force initially to the roll at a point remote from the central portion and the ends of the roll to deflect said portion in a direction opposite to its normal deflection.

12. A method of driving a looped forming wire in a paper machine, which comprises engaging the underside 1 1 of said wire with a drive roll, rotating the roll to drive the wire, and bowing the shaft for the roll at a location between opposite ends of said shaft to deflect the central portion of the roll in a direction opposite to its normal deflection.

13. In a paper machine, a looped forming wire, a roll engaging the wire and having normally a central deflec tion, shaft means for the roll engaging the interior of the roll inwardly from one edge thereof and having a shaft portion extending outwardly from said edge, and bearing means engaging said shaft portion extending outwardly from said edge and applying a couple thereto to deflect said shaft means and relieve the normal deflection in the central portion of said r011.

lteferences Cited in the file of this patent UNITED STATES PATENTS Hodgkins Aug. 28, 1917 Von Reis July 26, 1932 Goulding -L-.. Sept. 23, 1952 Hornbostel Sept. 8,1953 McArn Apr. 27, 1954 Byrd Mar. 4, 1958- Hornbostel Sept. 9, 1958 Shapiro et a1 Aug. 4, 1959 Robertson Aug. 11, 1959 Robertson et a1. Nov. 22, 1960 FOREIGN PATENTS Great Britain Apr. 4, 1956 

2. IN A PAPER MACHINE, A TRAVELING BAND, A ROLL ENGAGING AND SUPPORTING THE BAND AND HAVING NORMALLY A CENTRAL DEFLECTION, SHAFT MEANS FOR SAID ROLL, BEARING MEANS RECEIVING SAID SHAFT MEANS, AND AXIALLY SPACED RELATIVELY MOVABLE FLUID ACTUATED MEANS ENGAGING SAID BEARING MEANS APPLYING A FORCE COUPLE TO SAID SHAFT MEANS TO RELIEVE THE NORMAL DEFLECTION IN SAID ROLL.
 12. A METHOD OF DRIVING A LOOPED FORMING WIRE IN A PAPER MACHINE, WHICH COMPRISES ENGAGING THE UNDERSIDE OF SAID WIRE WITH A DRIVE ROLL, ROTATING THE ROLL TO DRIVE THE WIRE, AND BOWING THE SHAFT FOR THE ROLL AT A LOCATION BETWEEN OPPOSITE ENDS OF SAID SHAFT TO DEFLECT THE CENTRAL PORTION OF THE ROLL IN A DIRECTION OPPOSITE TO ITS NORMAL DEFLECTION. 